Work assembling auxiliary appratus and work assembling method

ABSTRACT

A work-assembling auxiliary device for carrying out the matching of phases in the spline-coupling of a main shaft Sm of a transmission T to a crankshaft Sc of an engine E includes an output shaft  40  radially movably connected through an Oldham coupling  41  to an input shaft  30  connected to and rotated by a drive source. A chamfer  61   a  is provided at a tip end of a socket  61  mounted on the output shaft  40 , and in inserting the socket  61  into a socket hole h in a crank pulley Pc, the output shaft  40  is smoothly aligned with the crankshaft Sc by the action of the chamfer  61   a . Further, when the output shaft  40  is reciprocally rotated, the phases of the socket  61  and the socket hole h are smoothly matched with each other, whereby the engagement of the socket  61  and the socket hole h is achieved. Thus, even if a somewhat deviation exists between an axis of the crankshaft Sc of the engine E and an axis of the output shaft  40  of the work-assembling auxiliary device, the socket  61  of the output shaft  40  can be reliably engaged into the socket hole h in the crankshaft Sc.

FIELD OF THE INVENTION

The present invention relates to a work-assembling auxiliary deviceincluding an engage means capable of being brought into engagement witha to-be-engaged means provided in a rotary shaft of a work body totransmit a rotating force of a drive means to the rotary shaft of thework body through the engage means and the to-be-engaged means, and to awork-assembling process for assembling an engine and a transmission inan assembling line.

BACKGROUND ART

One example of means for carrying out an assembling operation byrotating the rotary shaft of the work body to adjust the phase of therotary shaft is a transmission-assembling station provided in a powerunit-assembling line for an automobile. When an engine assembly and atransmission assembly assembled in the assembling line are to beintegrally coupled to each other, an end of a main shaft of thetransmission assembly is spline-coupled into a shaft hole in acrankshaft of the engine assembly. In this case, if the phase of a malespline of the end of the main shaft and the phase of a female spline ofthe shaft bore in the crankshaft are not matched with each other, theassembling of the transmission assembly and the engine assembly cannotbe achieved. Therefore, it is necessary to match both of the phases witheach other.

To carry out this operation, in a conventional engine and a transmissionassembling apparatus described in Japanese Utility Model PublicationNo.3-37865, a socket is mounted at an end of an output shaft connectedto a drive source for rotation, and in a state in which the socket is inengagement in a socket hole provided in an end of a crankshaft, thedrive source is operated to continuously rotate the crankshaft in onedirection, and a fitting auxiliary device is mounted on the transmissionto match the phases of the socket and the socket hole.

In the above conventional assembling apparatus, however, the position ofan axis of the output shaft provided with the socket is fixed and hence,if there is an error such as a looseness produced in position of theengine supported in a pallet, the socket mounted at the end of theoutput shaft cannot be smoothly brought into engagement in the sockethole provided in the end of the crankshaft. For this reason, it isnecessary to match the phase of a male spline of the end of the mainshaft with the phase of a female spline of the shaft bore in thecrankshaft, and an operation for such matching is extremely troublesome.Moreover, in the conventional device, the crankshaft is continuouslyrotated in one direction and hence, an exclusive auxiliary device isrequired and for example, it is necessary to mount a swinging device onthe transmission.

DISCLOSURE OF THE INVENTION

The present invention has been accomplished with the above circumstancesin view, and it is an object of the present invention to ensure thateven if a somewhat deviation exists between the axis of theto-be-engaged means provided in the rotary shaft of the work body andthe axis of the engage means of the work-assembling auxiliary device,the engage means can be reliably brought into engagement with theto-be-engaged means. It is another object of the present invention toensure that in spline-coupling the end of the crankshaft of the engineand the end of the main shaft of the transmission to each other, thematching of phases in the spline-coupling can be carried out easily andreliably.

To achieve the above object, according to a first aspect and feature ofthe present invention, there is provided a work-assembling auxiliarydevice including an engage means capable of being brought intoengagement with a to-be-engaged means provided in a rotary shaft of awork body to transmit a rotational force of a drive means to the rotaryshaft of the work body through the engage means and the to-be-engagedmeans, characterized in that the auxiliary device comprises an inputshaft connected to the drive means, an output shaft having the engagemeans, a coupling for connecting the output shaft to the input shaft, sothat the output shaft can be moved radially in parallel to the inputshaft, a first repulsively biasing means for biasing the output shaft,so that the output shaft is lined up with the input shaft on the sameaxis, a second repulsively biasing means for biasing the engage means ina direction to engage the to-be-engaged means, and an engaging guidemeans provided on at least one of the engage means and the to-be-engagedmeans, the drive means causing the rotation of the input shaft through apredetermined angle and the stoppage of the input shaft for apredetermined time alternately and repeatedly.

With the above arrangement, when the engage means mounted at the end ofthe output shaft is moved to engage the to-be-engaged means provided inthe end of the rotary shaft of the work body, the output shaft is linedup with the input shaft on the same axis by the action of the firstrepulsively biasing means. When the engage means is put into abutmentagainst the to-be-engaged means, the engaging guide means provided on atleast one of the engage means and the to-be-engaged means is guided tothe other of the engage means and the to-be-engaged means. Therefore, aradial load aligning the output shaft with the rotary shaft isgenerated, whereby the output shaft is moved radially in parallel to theinput shaft by the action of the coupling against the biasing force ofthe first repulsively biasing means and thus, the engage means isaligned automatically with the to-be-engaged means. At this time, if thephases of the engage means and the to-be-engaged means are matchedunexpectedly with each other, the engage means can be engaged with theto-be-engaged means. However, in many cases, the engage means cannot beengaged with the to-be-engaged means due to the mismatching of theirphases, and the second repulsively biasing means is compressed togenerate a biasing force in a direction to permit the engagement of theengage means with the to-be-engaged means.

When the rotation of the input shaft through a predetermined angle andthe stoppage of the member for a predetermined time are conductedalternately and repeatedly from this state by the drive means, a drivingforce is transmitted to the output shaft moved radially in parallel tothe input shaft by the action of the coupling, and at the moment thephase of the engage means mounted on the rotating output shaft ismatched with the phase of the to-be-engaged means, the engage means isengaged with the to-be-engaged means by the biasing force of the secondrepulsively biasing means. As described above, the engage means of theoutput shaft can be reliably engaged with the to-be-engaged means of therotary shaft only by positioning the axis of the output shaft and theaxis of the rotary shaft roughly rather than accurately, and moreover,the rotation of the input shaft can be reliably transmitted to theoutput shaft by the action of the coupling.

According to a second aspect and feature of the present invention, inaddition to the first feature, the coupling includes a drivingcylindrical member fixed to the input shaft, a follower cylindricalmember fixed to the output shaft and opposed to the driving cylindricalmember, a first guide pin fixed to the driving cylindrical memberperpendicularly to the axis, a second guide pin fixed to the followercylindrical member perpendicularly to the axis and the first guide pin,and a guide block through which the first and second guide pins areslidably passed.

With the above arrangement, even if the axis of the output shaft havingthe follower cylindrical member fixed thereto is deviated from the axisof the input shaft having the driving cylindrical member fixed thereto,the first guide pin mounted on the driving cylindrical member is slid ina slide block, and the second guide pin mounted on the followercylindrical member perpendicularly to the first guide pin is slid in theslide block, whereby the rotation of the input shaft can be transmittedto the output shaft without hindrance.

According to a third aspect and feature of the present invention, inaddition to the second feature, a plurality of the first guide pins anda plurality of the second guide pins are disposed in a planeperpendicular to the axis.

With the above arrangement, the plurality of first guide pins and theplurality of second guide pins are disposed in the plane perpendicularto the axis and hence, the swinging movements of the driving cylindricalmember and the follower cylindrical member relative to the guide blockcan be limited to ensure the parallelism of the input shaft and theoutput shaft.

According to a fourth aspect and feature of the present invention, inaddition to the second feature, the first repulsively biasing meansincludes two rods biased in a direction toward the axis by a spring, andtwo rollers mounted at tip ends of the rods to abut from the belowagainst two different points on an outer peripheral surface of each ofthe driving cylindrical member and the follower cylinder member of thecoupling for rolling movement, each of the rollers being put intoabutment against the outer peripheral surfaces of both the drivingcylindrical member and the follower cylinder member to permit the inputshaft and the output shaft to be lined up with each other on the axis.

With the above arrangement, the first repulsively biasing meansrepulsively brings the two rollers into abutment against the outerperipheral surfaces of the driving cylindrical member and the followercylinder member of the coupling. Therefore, when no radial load isapplied to the output shaft, the output shaft and the input shaft can belined up with each other on the axis against a force of gravity appliedto the output shaft.

According to a fifth aspect and feature of the present invention, inaddition to any of the first to fourth features, the drive means isdriven by a hydraulic cylinder, and a hydraulic and pneumatic pressureconverter for converting a pneumatic pressure into a hydraulic pressureis interposed between a pneumatic pressure source and the hydrauliccylinder.

With the above arrangement, the hydraulic and pneumatic pressureconverter for converting the pneumatic pressure into the hydraulicpressure is interposed between the pneumatic pressure source and thedrive means comprising the hydraulic cylinder. Therefore, the drivemeans can be driven at a constant speed irrespective of the magnitude ofa load to prevent the rapid rotation of the output shaft. Moreover, aninfluence of a difference between the area of a piston of the hydrauliccylinder adjacent the output rod and the area of the piston on the sideopposite from the output rod and other problems attendant on thecompressibility of air can be eliminated by the action of the hydraulicand pneumatic pressure converter.

According to a sixth aspect and feature of the present invention, inaddition to any of the first to fifth features, the work body is anengine; the rotary shaft is a crankshaft, and the to-be-engaged means isa socket hole defined at the center of a crank pulley.

With the above arrangement, the engage means can be brought intoengagement in the socket hole defined at the center of the crank pulleymounted on the crankshaft of the engine, whereby the crankshaft can berotated by the drive means.

According to a seventh aspect and feature of the present invention, inaddition to the sixth feature, a torque converter is integrally providedat an end of the crankshaft of the engine opposite from the crankpulley, and in a state in which the engage means of the output shaft isin engagement in the socket hole in the crank pulley, a main shaft of atransmission is spline-coupled into a shaft bore in the torqueconverter, while rotating the crankshaft.

With the above arrangement, the main shaft of the transmission can bespline-coupled reliably into the shaft bore in the torque converterintegrally provided at the end of the crankshaft opposite from the crankpulley by rotating the crankshaft by the drive means.

According to an eighth aspect and feature of the present invention,there is provided a work-assembling process for assembling an engine anda transmission in an assembling line, characterized in that the processcomprises the steps of bringing an engage means connected to a drivemeans into engagement with a to-be-engaged means formed at one of endsof a crankshaft of an engine, and conducting the rotation of thecrankshaft through a predetermined angle and the stoppage of thecrankshaft for a predetermined time alternately and repeatedly by thedrive means, thereby spline-coupling the other end of the crankshaft andan end of a main shaft of a transmission to each other.

With the above feature of the process, in bringing the engage meansconnected to the drive means into engagement with the to-be-engagedmeans formed at one of the ends of the crankshaft of the engine, androtating the crankshaft by the drive means, thereby spline-coupling theother end of the crankshaft and the end of the main shaft of thetransmission to each other, a phase-matching operation on the side ofthe spline of the main shaft can be smoothened by conducting therotation of the crankshaft through a predetermined angle and thestoppage of the crankshaft for a predetermined time alternately andrepeatedly.

According to a ninth aspect and feature of the present invention, inaddition to the eighth feature, the crankshaft is rotated forreciprocation by the drive means.

With the above feature, the crankshaft is rotated for reciprocation bythe drive means and hence, the phase-matching operation on the side ofthe spline of the main shaft can be simplified to smoothly achieve thespline coupling.

According to a tenth aspect and feature of the present invention, inaddition to the eighth feature, the crankshaft is rotated intermittentlyin one direction by the drive means.

With the above feature, the crankshaft is rotated intermittently in onedirection by the drive means and hence, the phase-matching operation onthe side of the spline of the main shaft can be simplified to smoothlyachieve the spline coupling.

Meanwhile, a follower shaft 30 in an embodiment corresponds to the inputshaft of the present invention; an Oldham coupling in the embodimentcorresponds to the coupling of the present invention; a followercylindrical member-supporting means 63 in the embodiment corresponds tothe first repulsively biasing means of the present invention; a spring45 in the embodiment corresponds to a second repulsively biasing meansof the present invention; a socket 61 in the embodiment corresponds tothe engage means of the present invention; a chamfer 61 a in theembodiment corresponds to the engaging guide means of the presentinvention; an engine E in the embodiment corresponds to the work body ofthe present invention; a socket hole h in the embodiment corresponds tothe to-be-engaged means of the present invention; and a crankshaft Sc inthe embodiment corresponds to the rotary shaft of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1 to 15 show an embodiment of the present invention, wherein FIG.1 is a side view of a transmission-assembling line;

FIG. 2 is a view taken along a line 2-2 in FIG. 1;

FIG. 3 is a view taken along a line 3-3 in FIG. 2;

FIG. 4 is a view taken along a line 4-4 in FIG. 3;

FIG. 5 is an enlarged view of an essential portion shown in FIG. 2;

FIG. 6 is an enlarged view of an essential portion shown in FIG. 2;

FIG. 7 is a view taken in the direction of an arrow 7 in FIG. 6;

FIG. 8 is a sectional view taken along a line 8-8 in FIG. 6;

FIG. 9 is a view taken along a line 9-9 in FIG. 6;

FIG. 10 is a sectional view taken along a line 10-10 in FIG. 9;

FIG. 11 is a sectional view taken along a line 11-11 in FIG. 6;

FIG. 12 is a sectional view taken along a line 12-12 in FIG. 11;

FIG. 13 is a view taken in the direction of an arrow 13 in FIG. 11;

FIG. 14 is a diagram of a pneumatic pressure circuit for an engine andtransmission assembling apparatus; and

FIG. 15 is an illustration for explaining the operation.

DESCRIPTION OF THE PREFERRED EMBODIMENT

The present invention will now be described by way of an embodiment ofthe present invention with reference to the accompanying drawings.

Referring to FIG. 1, a take-in station Si, a transmission-assemblingstation Sa and a take-out station So are provided in a transporting pathin a pallet conveyor Cp for transporting a pallet P having an engine Eplaced thereon. An engine E assembled in an engine-assembling line ishung down by a hanger He1 of an engine taking-in overhead conveyor Ce1and transported into the take-in station Si, where the engine E istransferred onto the pallet P on the pallet conveyor Cp. A transmissionT assembled in a transmission-assembling line is hung down by a hangerHt of a transmission taking-in overhead conveyor Ct and transported intothe transmission-assembling station Sa, where the transmission T isassembled to the engine E. The engine E having the transmission Tassembled thereto is transported to the take-out station So by thepallet conveyor Cp, where the engine E is turned about a vertical axisthrough an angle of 90°. Then, the engine E is hung by a hanger He2 ofan engine taking-out overhead conveyor Ce2 and transported from thetake-out station So.

As shown in FIGS. 2 to 5, in the transmission-assembling station Sa, anengine and transmission assembling device CD according to the presentinvention is disposed on one of sides of the transporting path in thepallet conveyor Cp, and the transmission T hung by the hanger Ht of thetransmission taking-in overhead conveyor Ct is disposed on the otherside of the transmitting path. A crankshaft Sc of the engine E isdisposed in a direction perpendicular to a transporting direction of thepallet conveyor Cp, and a crank pulley Pc for driving variousauxiliaries through an endless belt is mounted at an end of thecrankshaft Sc opposed to the engine and transmission assembling deviceCD. A hexagonal socket 61 provided at an end of an output shaft 40 ofthe engine and transmission assembling device CD is engaged into ahexagonal socket hole h provided at the center of the crank pulley Pc(see FIG. 5).

An operator pushes the transmission T hung by the hanger Ht of thetransmission taking-in overhead conveyor Ct, thereby inserting an end ofa main shaft Sm of the transmission T into a shaft bore Tca in a torqueconverter TC mounted at an end of the crankshaft Sc of the engine E.When the engine and transmission assembling device CD is operated inthis state to rotate the crankshaft Sc of the engine E, a male spline inthe end of the main shaft Sm is matched in phase with a female spline inthe shaft bore Tca in the torque converter TC, whereby the transmissionT is coupled to the engine E (see FIG. 15).

The pallet P includes a lower member 100 placed on the pallet conveyorCp, an upper member 102 rotatably supported on an upper surface of thelower member 100 with an angular roller bearing 101 interposedtherebetween, and a circular base plate 103 fixed to an upper surface ofthe upper member 102. A first engine-supporting member 106 is mounted onguide rails 104, 104 fixed to an upper surface of the base plate 103with sliders 105, 105 interposed therebetween. The position of the firstengine-supporting member 106 along the guide rails 104, 104 is capableof being adjusted by changing the position of a bolt 108 threadedlyfitted into any of a plurality of bolt bores in a nut member 107 fixedto the base plate 103. A second engine-supporting member 113 and a thirdengine-supporting member 114 are mounted on guide rails 109 and 110fixed to the upper surface of the base plate 103 with sliders 111 and112 interposed therebetween, respectively. The positions of the secondand third engine-supporting members 113 and 114 along the guide rails109 and 111 are capable of being adjusted by changing the positions ofbolts 117 and 118 each threadedly fitted in any of a plurality of boltsbores in each of nut members 115 and 116 fixed to the base plate 103.

Therefore, the position of the crankshaft Sc of the engine E can bealigned on a centerline of the pallet P by adjusting the positions ofthe first, second and third engine-supporting members 106, 113 and 114depending on the type of the engine E to be mounted on the pallet P. Thepositioning of the crankshaft Sc of the engine E mounted on the pallet Pis achieved by bringing a side of an oil pan into abutment against astopper 119 fixed to the base plate 103.

The structure of the engine and transmission assembling device CD willbe described below with reference to FIGS. 6 to 14.

A pair of slide guides 12, 12 and a lifting and lowering cylinder 13 aresupported on a lower surface of a horizontal support plate 11 of a baseframe 10 fixed to a floor surface, and a lift table 15 is fixed to upperends of slide rods 14, 14 vertically slidably fitted in the slide guides12, 12, and is connected to an output rod 13 a of the lifting andlowering cylinder 13, so that it can be lifted and lowered. A slidetable 18 is supported on two guide rails 16, 16 fixed to an uppersurface of the lift table 15 for movement in a longitudinal direction (adirection toward and away from the engine E) through slide guides 17,17. The slide table 18 is connected to an output rod 20 a of anadvancing and retracting cylinder 20 supported on the lift table 15 witha mounting bracket 19 interposed therebetween, so that it can beadvanced and retracted.

A support member 21 comprising a combination of a support plate 21 a,two reinforcing plate 21 b, 21 b and a bottom plate 21 c is fixed to anupper surface of the slide table 18, and a drive shaft 23 is rotatablysupported on a side of the support plate 21 a with two bearings 22, 22interposed therebetween. A slider 25 is vertically slidably carried on aslide guide 24 mounted in a rising manner on an upper surface of theslide table 18, and a rack 25 a provided on the slider 25 is meshed witha pinion 26 provided at an intermediate portion of the drive shaft 23.The slide guide 24 has a split groove 24 a which opens into an uppersurface thereof, and a clearance between the slide guide 24 and theslider 25 is adjusted by clamping two spacers 27, 27 fitted in the splitgrooves 24 a by two bolts 37, 37. The slider 25 supporting the rack 25 ais connected to an output rod 29 a of a rotating cylinder 29 supportedin a turned-up attitude on a lower surface of the slide table 18 withbrackets 28, 28 interposed therebetween, so that it can be lifted andlowered.

A longitudinally extending follower shaft 30 is supported at upper endsof two support posts 31, 31 rising on the upper surface of the slidetable 18 with bearings 32, 32 interposed therebetween. A drive sprocket33 mounted at an end of the drive shaft 23 and a follower sprocket 34mounted at an end of the follower shaft 30 are connected to each otherby an endless chain 35, and a tension sprocket 36 supported on a side ofa support plate 38 rising on an upper surface of the slide table 18 ismeshed with an inner peripheral surface of the endless chain 35.Therefore, when the rotating cylinder 29 is driven in expanding orcontracting movement to lift or lower the rack 25 a, the drive shaft 23and the drive sprocket 33 are rotated along with the pinion 26 meshedwith the rack 25 a. The rotation of the drive sprocket 33 is transmittedto the follower sprocket 34 through the endless chain 35, whereby thefollower shaft 30 integral with the follower sprocket 34 is rotated. Apower-transmitting path extending from the rotating cylinder 29 to thefollower shaft 30 constitutes a drive means D of the present invention.

The follower shaft 30 and the output shaft 40 are connected to eachother through an Oldham coupling 41. The Oldham coupling 41 connects adriving cylindrical member 42 fixed to an end of the follower shaft 30and a follower cylindrical member 44 spline-coupled 43 to the outputshaft 40. The output shaft 40 is supported relatively non-rotatably andaxially slidably on a shaft portion 44 a of the follower cylindricalmember 44. The output shaft 40 is biased in a protruding direction by aspring 45 mounted under compression between the output shaft 40 and afront end of the follower cylindrical member 44, and a pin 46 extendingthrough a rear end of the output shaft 40 in a direction perpendicularto an axis L of the follower shaft 30 and the output shaft 40 isslidably fitted into an elongated bore 44 b defined in the shaft portion44 a of the follower cylindrical member 44, thereby limiting the rangeof axial sliding movement of the output shaft 40.

Two first guide pins 47, 47 extending in a direction perpendicular tothe axis L are fixed in parallel to the driving cylindrical member 42.To prevent slipping-off of the first guide pins 47, 47, a stationaryplate 48 engaged in notches defined in the first guide pins 47, 47 isfixed to an outer surface of the driving cylindrical member 42 by bolts49, 49. Likewise, two second guide pins 50, 50 extending in a directionperpendicular to the axis L are fixed in parallel to the followercylindrical member 44. To prevent slipping-off of the second guide pins50, 50, a stationary plate 51 engaged in notches defined in the secondguide pins 50, 50 is fixed to an outer surface of the followercylindrical member 44 by bolts 52, 52. The two first guide pins 47, 47fixed to the driving cylindrical member 42 and the two second guide pins50, 50 fixed to the follower cylindrical member 44 are slidably passedthrough a guide block 53 accommodated in the driving cylindrical member42 and the follower cylindrical member 44. The first guide pins 47, 47fixed to the driving cylindrical member 42 and the second guide pins 50,50 fixed to the follower cylindrical member 44 are perpendicular to eachother as viewed in a direction of the axis L.

Follower cylindrical member-supporting means 63, 63 for retaining thefollower cylindrical member 44 coaxially with the driving cylindricalmember 42 are provided on the upper surface of the slide table 18. Eachof the left and right follower cylindrical member-supporting means 63,63 has two left and right rods 55 slidably supported on two stays 54, 54fixed to the upper surface of the slide table 18. The left and rightrods 55 extend in a direction pointing to the axis L to form an angle of90° by each other. Rollers 59, 59 are rotatably supported through rollershafts 58, 58 on the brackets 57, 57 mounted at tip ends of the left andright rods 55 biased in the protruding direction by springs 56.

Therefore, the centerline of the driving cylindrical member 42 is alwaysconcentric with the axis L of the follower shaft 30, while thecenterline of the follower cylindrical member 44 is movable radiallyrelative to the axis L under the action of the Oldham coupling 41. Inthis case, the centerline of the follower cylindrical member 44 isalways maintained parallel to the centerline of the driving cylindricalmember 42, because the two first guide pins 47, 47 are provided on thedriving cylindrical member 42 and slidably passed through the guideblock 53, and the two second guide pins 50, 50 are provided on thefollower cylindrical member 44. The follower cylindrical member 44 isretained concentrically with the driving cylindrical member 42 in ausual state (when no radial load is applied to the output shaft 40) byabutment of the pair of rollers 59, 59 pushing up the followercylindrical member 44 from the oblique and below against the outerperipheral surface of the driving cylindrical member 42.

A socket 61 hexagonal in section and capable of being engaged into thesocket hole h (see FIG. 5) hexagonal in section and provided in thecrank pulley Pc is fixed to a flange 60 fixed to a tip end of the outputshaft 40 by a plurality of bolts 62. To ensure the smooth engagement ofthe socket 61 in the socket hole h, a tapered chamfer 61 a is providedat a tip end of the socket 61.

A pneumatic pressure circuit for the lifting and lowering cylinder 13,the advancing and retracting cylinder 20 and the rotating cylinder 29 isshown in FIG. 14. A pilot pressure pipe 71 connected to a pneumaticpressure source 70 and an exhaust pressure pipe 73 connected to asilencer 72 are connected to the lifting and lowering cylinder 13comprising a pneumatic cylinder through a switchover valve 74 andone-way throttle valves 75, 75. The pilot pressure pipe 71 and theexhaust pressure pipe 73 are connected to the advancing and retractingcylinder 20 comprising a pneumatic cylinder through a switchover valve76 and one-way throttle valves 77, 77 and are connected to the rotatingcylinder 29 comprising a hydraulic cylinder through a switchover valve78, hydraulic and pneumatic pressure converters 79, 79 and one-waythrottle valves 80, 80.

Therefore, when the switchover valve 74 is in a central position shownin FIG. 14, the lifting and lowering cylinder 13 is in a stopped state.When the switchover valve 74 is moved rightwards from the centralposition, the lifting and lowering cylinder 13 is contracted to lowerthe lift table 15. When the switchover valve 74 is moved leftwards fromthe central position, the lifting and lowering cylinder 13 is expandedto lift the lift table 15. In this manner, the level of the lift table15 can be adjusted to any level depending on the type of the engine E.When the switchover valve 76 is in a right position shown in FIG. 14,the advancing and retracting cylinder 20 is contracted to retract theslide table 18. When the switchover valve 76 is shifted to a leftposition, the advancing and retracting cylinder 20 is expanded toadvance the slide table 18. In this manner, the slide table 18 can bereciprocally moved between a retracted position and an advancedposition. When the switchover valve 78 is in a right position shown inFIG. 14, the rotating cylinder 29 is contracted to rotate the outputshaft 40 in a clockwise direction. When the switchover valve 78 isshifted to a left position, the rotating cylinder 29 is expanded torotate the output shaft 40 in a counterclockwise direction. In thismanner, the output shaft 40 can be reciprocally rotated between twopositions.

When the output shaft 40 is rotated by the rotating cylinder 29, a largestatic frictional force provided by a repulsing force of the spring 45is applied to an area of contact between the socket 61 mounted on theoutput shaft 40 and the socket hole h and hence, the socket 61 and thesocket hole h cannot be rotated relative to each other. In order toprevent the rotating cylinder 29 from being operated at a stroke torotate the output shaft 40 suddenly, when the load of the rotatingcylinder 29 is increased to permit the slight relative rotation of thesocket 61 and the socket hole h, resulting in sudden decreasing of thecoefficient of friction, hydraulic and pneumatic pressure converters 79,79 are interposed between the pneumatic pressure source 70 and therotating cylinder 29 in the present embodiment. Thus, the rotatingcylinder 29 can be driven at a constant speed by an uncompressibleworking oil, and the sudden rotation of the output shaft 40 can beprevented. An influence of a difference between the area of a piston ofthe rotating cylinder 29 adjacent the output rod 29 a and the area ofthe piston on the opposite side from the output shaft 29 a can becompensated for by the hydraulic and pneumatic pressure converters 79,79, and other problems attendant on the compressibility of the air canbe eliminated.

The operation of the embodiment of the present invention having theabove-described arrangement will be described below.

Referring to FIG. 1, the engine E hung and transported by the hanger He1of the engine taking-in overhead conveyor Ce1 is placed onto the palletP at the take-in station Si and transported into thetransmission-assembling station Sa by the pallet conveyor Cp. In asynchronism with this, the transmission T hung by the hanger Ht of thetransmission taking-in overhead conveyor Ct is transported into thetransmission-assembling station Sa.

At this time, the axis of the crankshaft Sc of the engine E supported onthe first, second and third engine support members 106, 113 and 114mounted on the pallet P has been located on the centerline of the palletP as viewed in a plane by previously adjusting the positions of thefirst, second and third engine support members 106, 113 and 114.Therefore, when the pallet P is stopped at a predetermined position inthe transmission-assembling station Sa, the axis of the crankshaft Sc ofthe engine E is aligned, as viewed in plane, with the axis of the outputshaft 40 of the engine and transmission-assembling apparatus CD mountedin the transmission-assembling station Sa (see FIG. 2). In addition, thelevel of the output shaft 40 of the engine and transmission-assemblingapparatus CD is matched with the level of the crankshaft Sc of theengine E on the pallet P by previously operating the lifting andlowering cylinder 13 to lift or lower the lift table 15.

Even if the axis of the output shaft 40 and the axis of the crankshaftSc are slightly deviated from each other due to a cause such as themisalignment of the engine E on the pallet P when theadvancing/retracting cylinder 20 has been driven from the just-describedstate to advance the slide table 18 toward the pallet P in order tobring the socket 61 mounted at the tip end of the output shaft 40 intoengagement in the socket hole h in the crankshaft Sc, an aligningfunction for aligning both of the axes with each other by the chamfer 61a formed at the tip end of the socket 61 contacting with the socket holeh is exhibited, whereby a radial reaction force is applied from thesocket hole h to the socket 61. As a result, the output shaft 40 ismoved radially in parallel to the axis L of the follower shaft 30through the Oldham coupling 41, whereby the output shaft 30 and thecrankshaft Sc are concentrically lined up with each other.

However, the phase of the socket 61 and the phase of the socket hole hare not matched with each other in many cases and hence, it is seldomthat the socket 61 is brought into complete engagement in the sockethole h, and the output shaft 40 is retracted into the shaft portion 44 aof the follower cylindrical member 44 in response to the advancement ofthe slide table 18, while compressing the spring 45. Since the rotatingcylinder 29 is driven in an extendable manner from this state to conductthe rotation of the follower shaft 30 through a predetermined angle andthe stoppage of the follower shaft 30 for a predetermined timealternately and repeatedly, the output shaft 40 eccentric from thefollower shaft 30 is rotated intermittently and reciprocally through theOldham coupling 41, whereby the socket 61 mounted on the output shaft 40is rotated intermittently and reciprocally, so that the phase thereof ismatched with the phase of the socket hole h. Then, the output shaft 40biased by the repulsing force of the spring 45 is allowed to protrudeforwards, whereby the socket 61 is brought into engagement in the sockethole h.

When the rotational direction is changed by intermittently andreciprocally rotating the output shaft 40 in the above manner, theoutput shaft 40 is decelerated and once stopped, and then rotated againin the opposite direction. Therefore, the chance of engagement of thesocket 61 and the socket hole h with each other can be increased toenable the smooth coupling.

When the socket 61 has been brought into engagement in the socket hole hin the above manner, the end of the main shaft Sm of the transmission Tis inserted into the shaft bore TCa in the torque converter TC of theengine E, as shown in FIG. 15, by pushing the transmission T hung by thehanger Ht of the transmission taking-in conveyor Ct by an operator. Atthis time, the phase of the male spline of the main shaft Sm and thephase of the female spline of the shaft bore TCa are not matched witheach other in most cases and in usual, it is seldom that both of thesplines are smoothly brought into engagement with each other. Therefore,the rotating cylinder 29 is driven intermettently in an extendablemanner to conduct the rotation of the follower shaft 30 through apredetermined angle and the stoppage of the follower shaft 30 for apredetermined time alternately and repeatedly, whereby the crankshaft Scis rotated intermittently and reciprocally through the follower shaft30, the Oldham coupling 41, the output shaft 40, the socket 61 and thesocket hole h. When the phases of the splines of the crankshaft Sc andthe main shaft Sm are thus matched with each other, the crankshaft Scand the main shaft Sm are brought into complete engagement with eachother. Then, the engine E and the transmission T are fastened to eachother by the plurality of bolts 64 and in this manner, the operation forassembling the transmission T to the engine E is completed.

As described above, even if there is a somewhat error in the position ofthe crankshaft Sc of the engine E placed on the pallet P, the outputshaft 40 provided with the socket 61 follows the position of thecrankshaft Sc to become aligned automatically. Therefore, the socket 61can be brought into engagement in the socket hole h without troublingthe operator, leading to a remarkably enhanced operability.

The engine E having the transmission T assembled thereto is transportedto the take-out station So by the pallet conveyor Cp, where the baseplate 103 of the pallet P is turned through 900 to change the attitudeof the engine E. Then, the engine E is transferred onto the hanger He2of the engine taking-out overhead conveyor Ce2 for transportation.

Although the embodiment of the present invention has been described indetail, it will be understood that the present invention is not limitedto the above-described embodiment, and various modifications in designmay be made without departing from the spirit and scope of the inventiondefined in claims.

For example, the output shaft 40 is intermittently and reciprocallyrotated through a rotational angle of 180° in the embodiment, but therotational angle may be changed to any value. Further, the output shaft40 may be rotated intermittently in one direction. In this case, anelectric motor or the like may be used in place of the rotating cylinder29.

The chamfer 61 a is provided at the tip end of the socket 61 in theembodiment, but a chamfer may be provided at an opening of the sockethole h, or chamfers may be provided at the tip end of the socket 61 andat the opening of the socket hole h, respectively.

The structure of the Oldham coupling 41 for coupling the follower shaft30 and the output shaft 40 to each other is not limited to that in theembodiment, and other type of a coupling having a similar function maybe employed.

INDUSTRIAL APPLICABILITY

The present invention is most effectively applicable to an operation forspline-coupling the end of the main shaft of the transmission assemblyinto the shaft bore in the crankshaft of the engine assembly, but isapplicable to any work body other than the engine body in claims 1 to 5of the present invention.

1. (canceled)
 2. (canceled)
 3. (canceled)
 4. (canceled)
 5. (canceled) 6.(canceled)
 7. (canceled)
 8. (canceled)
 9. (canceled)
 10. (canceled) 11.A work-assembling auxiliary device including an engage means (61)capable of being brought into engagement with a to-be-engaged means (h)provided in a crankshaft (Sc) of an engine (E) to transmit a rotationalforce of a drive means (D) to said crankshaft (Sc) of the engine (E)through said engagement means (61) and said to-be-engaged means (h),thereby spline-coupling a main shaft (Sm) of a transmission (T) to atorque converter (TC) integrally provided on an end of said crankshaft(Sc) opposite from said to-be-engaged means (h), characterized in thatsaid work-assembling auxiliary device comprises: an input shaft (30)connected to said drive means (D), an output shaft (40) having saidengagement means (61), a coupling (41) for connecting said output shaft(40) to said input shaft (30), so that said output shaft (40) can bemoved radially in parallel to said input shaft (30), a first repulsivelybiasing means (63) for biasing said output shaft (40), so that saidoutput shaft (40) is lined up with said input shaft (30) on the sameaxis (L), a second repulsively biasing means (45) for biasing saidengage means (61) in a direction to engage said to-be-engaged means (h),and an engaging guide means (61 a) provided on at least one of saidengage means (61) and said to-be-engaged means (h), said drive means (D)causing the rotation of the input shaft (30) through a predeterminedangle and the stoppage of the input shaft (30) for a predetermined timealternately and repeatedly.
 12. A work-assembling auxiliary deviceaccording to claim 1, wherein said to-be-engaged means (h) is a socketbore (h) defined at the center of a crank pulley (Pc).
 13. Awork-assembling process for assembling an engine (E) and a transmission(T) in a assembling line, characterized in that said process comprisesthe steps of bringing an engage means (61) connected to a drive means(D) into engagement with a socket bore (h) defined at the center of acrank pulley (Pc) provided on one of ends of a crankshaft (Sc) of anengine (E), and conducting the rotation of said crankshaft (Sc) througha predetermined angle and the stoppage of said crankshaft (Sc) for apredetermined time alternately and repeatedly by said drive means (D),thereby spline-coupling the other end of said crankshaft (Sc) and an endof a main shaft (Sm) of a transmission (T) to each other.
 14. Awork-assembling process according to claim 3, wherein a torque converter(TC) is integrally provided at the other end of the crankshaft (Sc), anda shaft bore (Tca) in the torque converter (TC) and the end of the mainshaft (Sm) are spline-coupled to each other.